Paper bag tube severing machine



April 12, 1949. e. w. POPPE PAPER BAG TUBE SEVERING MACHINE 4 Sheets-Sheet 1 Filed 001;. 1 1, 1946 N nN mmv TOR. 620/4 W Pap/ 5 April 12, 1949. w, POPPE 2,466,823

PAPER BAG TUBE SEVERING MACHINE Filed 001;. 11, 1946 4 Sheets-Sheet 2 [i I INVENTOR. "1 GEORGE W poPPE 1* BY 770 NEYS 4 Sheets-Sheet 4 Filed Oct. 1 1, 1946 INVENTOR. 60P /4. Pia/ F4- w W ATTO/P/YfVS Patented Apr. 12, 1949 PAPER BAG TUBE SEVERING MACHINE George W. Poppe, Brooklyn, N. Y., assignor Equitable Paper Bag Co. Inc., Long Island City,

N. Y., a corporation of New York Application October 11, 1946, Serial No. 702,627

7 Claims. (Cl. 164-845) This invention relates to paper bag tube severing machine.

In one method of making paper bags, a paper web while being advanced lengthwise of the web is transversely weakened at predetermined longitudinal intervals, after which it is folded into tube form and separated along the weakened portion to form tubular bag blanks. Much difiiculty has been encountered in satisfactorily separating the tube bag blanks from the remainder of the web in the high speed production of large size bags.

An object of this invention is an improvement in the tube blank separating mechanism of bag' making machines by the use of which large, as

well as small bags, may be produced at high speed.

According to thi invention, the weakened tubulated web is simultaneously gripped between two sets of rollers with the weakened portion of the web interposed between the two sets. The timing of the rollers is such that the main body of the tubulated web is temporarily slowed down slightly while the bag blank to be separated is temporarily advanced at high .speed. The pull thu produced eflects separation of the bag blank from the remainder of the web which is immediately released and allowed to proceed at its normal speed. Means are provided to adjust the length of time that the tubulated web is slowed down to adapt the mechanism for the different production speeds incident to the formation of diflerent length bags.

Other objects, novel features and advantages of this invention will become apparent from the following specification and accompanying drawings, wherein:

. Fig. 1 is a vertical section through a machine embodying the invention;

Fig. 2 is a side elevation of a portion of the machine;

Fig. 3 is an enlarged fragmentary view similar to Fig. 1;

Fig. 4 is a plan view of the web at an intermediate stage in the production of the bags, and

Fig. 5 is a detail view.

A frame Ill supports a pair of bars II and I2, of which the bar II supports a roll of paper or other suitable web I3 while the bar I2 supports a pair of rolls of paper or other suitable web l4. By means subsequently to be described, the web I3 is transversely perforated and obliquely slit to outline the blank I5 shown in Fig. 4 and the two webs I4 are converted into patches IB and I1 pasted to the blank I5. In preparing the web I3 for the production of bags, the web is transversely perforated inwardly-from each edge along lines I8 and I9 and is also perforated transversely along the line 20, the latter line being spaced forwardly of the other two line and being of slightly less extent than the distance between the inner ends-of the other two lines. The web is'subsequently slit along lines 2| extending between the inner ends of the lines I8 and I9 and the outer ends of the line 20. The perforations and the slits together outline the blank it which eventually is formed into a bag.

After the web has been perforated, as above described, the patches I6 and I! are fixed thereto and later each patch, as well as that portion of the web I3 underlying the patch is die out along the dot-dash lines of Fig, 4 to form finger holes and locking tabs. After the application of the patches, the slits 2| are formed and the web is folded into tube form in the usual manner and later the blank I5 in tube form is brokenaway from the remainder of the tubulated web by means subsequently to be described.

From its supply roll, the web I3 is led around a guide roller and between a pair of perforating cylinders 22 which perforate the web along the lines I8, I9 and 2|]. From the perforating cylinders 22, the web passes around a backing roller 23 suitably arranged with respect to a paste-delivering roller 24 to supply a line of paste P along that edge of the web l3 at-which the perforation I9 begins. After the application of the paste line P, the web I3 passes between a backing roller 25 and a paste-delivering roller 26, by which paste is applied to the web over the areas to which the patches I6 and H are to be 'aflixed.

The webs I 4 lead from their supply rolls to a pair of feed rollers 21 which advance the webs ll to die rollers 28 which-sever the web into the patches I6 and I1. These patches, together with the web I3, are passed between a pair of feed and pressure rolls 29 with the patches in register with the paste areas on the web so that the patches are aflixed to the web. Next, the web l3, with the applied patches l6 and I1 passes between another pair of feed rollers 30 from which the web passes between a pair ofslitting cylinders 3| which slit the web' along the lines 2|. The web is now in condition for formation into a tube and for separation ofthe tube into bag sections.

From the rollers 3|, the web I3 with the applied patches I6 and I1, passes around a former plate 32 by means of which the edges of the web are folded inwardly into overlapping relation along the dotted lines a and b with the paste line P of the one folded-in portion engaging the outer surface of the other folded-in portion. After the web has been thus folded, the tubulated web passes between identical feed rollers 33 driven in unison by means hereinafter described and the feed rollers 29 and 30 as well as the upper slitting cylinder 3i, are driven from the feed rollers 33 by means (not shown) at the same surface speed as the rollers 33, while thefeed rollers 21 and the patch-cutting rollers 23 are rotated by means (not shown) at the proper rate to supply patches to the web at bag length intervals. The rate of feed of the web l3 through the machine is determined by the surface speed of the feed rollers 33. The feed rollers are of such design that they contact the tubulated web l3 only along the edges thereof.

After leaving the feed rollers 33, the tubulated web passes through mechanism by means of which it is separated into bag sections. This mechanism comprises a first pair of rollers 34 and 35 and a second pair of rollers 35 and 31 between which the tubulated web passes successively. The roller 34 is of slightly less diameter than the roller 35 and is provided with a pinch bar 38 projecting from its surface and extending from end to end of the roller. The pinch bar 38 may have its leading edge parallel to the roller axis or may be of the shape shown in Fig. in which its leading edge is in the shape of a flattened V with the apex thereof to the rear of the remainder. The bar 38 has a curved outer surface coaxial with the roller 34 and of the same radius as the roller 35. The arrangement is such that as the tubulated web 13 passes between the rollers 34 and 35, it is periodically gripped between the pinch bar 38 and the roller 35, but otherwise advances independently of the rollers at a rate depending upon the surface speed of the feed rollers 33.

The diameter of the roller 36 is twice that of the roller 31 which rotates twice for each rotation of the roller 36. The roller 36 is provided with an inset 39 projecting slightly beyond the roller surface and having a groove4il extending parallel to the roller axis. Diametrically opposite the groove 40, the roller 36 is provided with an arcuate recess 4| extending parallel to the roller axis. The roller 31 is provided with a scoring bar 42 extending parallel to its axis and projecting slightly beyond the roller surface. The arrangement is such that the scoring bar 42 registers alternately with the groove 40 and the recess 4| for each complete rotation of the roller 36 so that the web I3 is gripped between the inset 39 surface and the roller 31 once for each rotation of the roller 36 but otherwise advances independently of these rollers. The rollers 36 and 31 are provided with suitablemeans (not shown) for die cutting the web and patches along the dotdash lines of Fig. 4.

A gear 43 is fixed to the roller 36 and an identical gear 44 is rotatably supported by the frame Ill. Both gears 43 and 44 mesh with a gear 45 fixed to the roller 31. A gear 46 is fixed to the gear 44 and an identical gear 41 is fixed to the roller 35 in mesh with the gear 46. Each gear 46 and 41 is so mounted as to be adjustable from concentricity to different positions of eccentricity with respect to the axes of rotation of the gear 44 and the roller 35 respectively. The rollers 34 and 35 are interconnected by suitable gearing for rotation in unison. A gear 43 identical with the gear 44 and in mesh therewith is mounted on a shaft 49 driven at constant rotational speed by any suitable means (not shown). A gear 50 mounted on the shaft 49 meshes with a gear 5| which also meshes with a gear 52 rotatable with the bottom feed roller 33. The gear Si is journalled on a bracket 53 plvotally supported coaxial with the gear 52 and a gear 54 rotatable with the upper feed roller 33 is in mesh with the gear 52.

The roller 31 makes two complete revolutions for each complete revolution of each of the rollers 34, and 36. The arrangement is such that with the tubulated web l3 gripped between the inset 39 of the roller 36 and the roller 31, the web .is also gripped between the pinch bar 38 of the roller 34 and the roller 35 with one set of perforations l8, l9 and 20 and slit portions 2| of the web intermediate the two sets of rollers. The

radius of the pinch bar 38 surface and of the roller 35 is such that the surface speed thereof is substantially less than the surface speed of the roller 31 so that when the web is gripped by both sets of rollers that part of the tubulated web ahead of the perforations and slits is caused to move faster than the web is delivered by the feed rollers 33 and that part of the tubulated web following the perforations and slits is caused to move at a slower rate than the web is delivered by the feed rollers 33. As a result, tubulated blanks are successively pulled away from the tubulated web and there is a slight temporary back-up of the web between the feed rollers 33 and the pinch bar rollers. The severance of the tubulated blank from the tubulated web occurs immediately after the gripping of the tubulated blank by the rollers 36 and 31 and the gripping of the tubulated web by the rollers 34 and 35 and practically simultaneously with the severance operation the tubulated blank is scored and the patches as well as the underlying web are cut along the dot-dash lines of Fig. 4, after which the rollers 36 and 31 release the tubulated blank which is gripped by take-01f rollers (not shown) while the pinch bar rollers 34 and 35 release the tubulated web for advancement by the feed rollers 33 at the surface speed thereof. Upon the next full revolution of the roller 31, the scoring bar 42 registers with the recess 41 of the roller 36 so that the tubulated web is not gripped between the rollers 36 and 31 until the roller 36 completes a full revolution.

As previously set forth, the shaft 49, together with the gear 48 are driven at constant rotational speed and the machine is conditioned for the production of different length bags within a given range by varying the rate of feed of the web. Th change of the rate of feed of the web is effected by changing th gearing between the shaft 49 and the bottom feed roller 33. To do this, either a larger of smaller diameter gear 50 is substituted for the gear 50 shown in Fig. 2 and the bracket 53 is correspondingly adjusted to arrange the gear 5| in mesh with the substituted gear 50, the gear 5i always remaining in mesh with the gear 52. A large gear 50 causes faster rotation of the feed rollers 33 than a small diameter gear 56 and the desired rate of feed is obtained by making use of the proper size gear 50. In the production of the maximum length bag, the web I3 is advanced at higher speed than in the production of the minimum length bag. For any given web feed speed (dependent upon th length of the bag being produced), there is a surface speed of the pinch bar 38 and roller 35 which will delay the travel of the tubulated web sufliciently to effect severance of the tube blank l5 from the tubulated web l3 Without delaying the web feed unduly to caus an excess of web to be delivered into the space'between the feed rollers 33 and the pinch bar rollers of such magnitude as to result in suflicient distortion of the web to prevent proper operation of the machine. A longer web delay is needed for low web speeds to effect sufllcient relative movement of the tube blank and the tubulated web to effect severance of the tube blank from th tubulated web. A shorter web delay is needed for high web speeds to prevent undue back-up of web between the pinch bar rollers 34 and 35 and the feed rollers 33. Variation in the surface speed of the pinch bar 38 and roller 33 at the time of clamping the tubulated web is effected by adjustment of the gears 46 and 41.

With the gears 43 and 41 in the position shown in Fig. 2, the surface speed of the pinch bar 33 and the roller 35 at the time of clamping the web is maximum and with the gears in th opposite position of eccentricity, the surface speed of the pinch bar 38 and the roller 35 at the tim of gripping the web I 3 is minimum. For operation of the machine to produce maximum length bags, the arrangement of the gears 46 and 41 is as shown in Fig. 2 while, for the production of minimum length bags, the eccentricity of the gears 48 and 41 isjust opposite from that shown in Fig. 2. Thus,'the hold-back time is made minimum for high web feed speeds and maximum for low web speeds.

In the operation of the above-described separating mechanism, the pinch bar rollers 34 and .35 firmly grip the tubulated web across its entire width and create a slight slack between the pinch bar rollers and the feed rollers 33 thereby effectively preventing the transmission of any pull or jerk resulting from th separating operation to that section of the web contacting the heel of the former plate 32 where breakage frequently occurs along the weakened or perforated transverse sections of the web. Th possibility of distortion of the web to an extent to cause interruption of the machine operation is thus avoided. With this type of machine, it is possible to run a much heavier base weight paper than previously has been the case. Also, by reason of the positive gripping of th web by the pinch bar rollers and the temporary slowing down of the web, it is possible to produce bags nearly equal in length to the circumference of the rollers 33 as the slowing down of the web and'the positive gripping of it throughout its entire width by the pinch bar rollers 34 and 35 eifects separation of the tubulated blank from the tubulated web with the surface speed of the roller 36 exceeding the surface speed of the feed rollers 33 by only five per cent. Furthermore, by reason of the positive gripping of the web by the pinch bar rollers, the weakened lines l8 and i9 may be rows of very fine perforations since there is a positive pull over the full extent of the lines and a clean break results. In addition, there is no agitation of the web of a nature which might tend to displace the patches, the paste for which has not had time to set during the period between its application and the blank severing operation. With the pinch bar of Fig.

5, the added advantage is obtained ofhaving the severing pull applied first to the edges of the web so as to start severance easily by a shearing action, at the outer ends of the weakened lines and progress inwardly toward the middle. This action is the result of having the leading edge of the pinch barconverge rearwardly from both ends toward the middle.

I claim:

1. A machine including the combination of a feeder for continuously pushing a traveling web of flexible material from it, a speed-up device spaced from said feeder for gripping said material fed therefrom and intermittently forcing the gripped portion thereof to a. higher traveling speed than is imparted by said feeder, a slowdown device between said feeder and said speedup device for gripping said material and intermittently forcing the gripped portion thereof to a slower traveling speed than is imparted by said feeder, whereby said material'is intermittently tensioned to sever a length of said material from the remainder and whereby an excess of said material intermittently collects between said.

feeder and said slow-down device in synchronism with the latter's operation and said tension is isolated from said feeder by said excess of said material, and including a system for variably fixing the material feeding speed of said feeder independently of the frequency of the described intermittent operations of said devices whereby to vary the length of the severed material.

2. The machine defined by claim 1 with said machine further including a system for adjustably fixing the amount of slow-down action of said slow-down device relative the material feeding speed of said feeder, whereby to adjustably fix the amount of said excess of said material which intermittently collects between said feeder and said slow-down device. I

3. The machine defined by claim 1 with said combination further including a system for variably fixing the material feeding speed of said feeder independently of the frequency of the described intermittent operations of said devices whereby to vary the length of the severed material, and a system for adjustably fixing the amount of slow-down action of said slow-down device relative the materialfeeding speed of said feeder, whereby to adjustably flx the amount of said excess of said product which intermittently collects between said feeder and said slow-down device.

4. A machine including the combination of a rotary feeder for continuously feeding a flexible web by pushing it therefrom, a speed-up rotary gripper device spaced from said feeder for periodically gripping said web and controlling the speed of the gripped portion of said web, a slow-down rotary gripper device positioned between said speed-up device and said feeder for periodically gripping said web and controlling the speed of the thereby gripped portion of said web, and rotary gearing intergearing said devices for synchronous gripping operation with a gear ratio causing said speed-up device to have a faster webcontrolling speed than said slow-down device and for. intergearing said feeder with said devices with a gear ratio causingv it to have a feeding speed faster than the web-controlling speed of said slow-down device and slower than the webcontrolling speed of said speed-up device, said gearing having a gear train for said feeder which includes two intermeshed gears with one thereof mounted on a, bracket pivoted at the axis of the other so it may swing while continuously meshing with said other gear and a shaft positioned for mounting a third gear intermeshing with said swinging gear and having releasable gear mounting means permitting releasable application of gears having a range of diameters.

5. The machine defined by claim 4 with said gearing having a gear train for said slow-down gripper including intermeshing gears of equal pitch diameters and which are radially shiftable from their rotating axes in similar directions angularly correlated with the active part of said rotary slow-down gripper to cause speed changing thereof during its material gripping phase.

6. The machine defined by claim 4 with said gearing having a gear train for said feeder which includes two intermeshed gears with one thereof mounted on a bracket pivoted at the axis of the other so it may swing while continuously meshing with said other gear and a shaft positioned for mounting a third gear intermeshing with said swinging gear and having releasable gear mountgripped thereby, and gearing between said grippers for synchronous operation and including two gear elements of equal pitch diameters which intergear and are radially shiftable from their rotating axes in similar directions, angularly correlated with the active part of said gripper to cause speed changing thereof, whereby the webcontrolling speed ratio between said devices may be controlled without loss of synchronization of pitch diameters, and with said devices cooperative gripping action.

GEORGE W. POPPE.

REFERENCES CITED The following references are of record in the file of this patent:

UNITED STATES PATENTS Number Name Date 2,013,086 Baker Sept. 3, 1935 2,060,450 Steen Nov. 10, 1936 2,101,191 Poppe Dec. '7, 1937 2,124,209 Poppe July 19, 1938 2,129,842 Holweg Sept. 13, 1938 2,216,212 Potdevin et al Oct. 1, 1940 2,328,582 Ratchford et al. Sept. 7, 1943 

